Fluid pressure control system



Dec. 15,l 1936. J 1 KUND|G 2,064,379,

FLUID PRESSURE CONTROL SYSTEL original Filed Jan. 1o, 1931 2 sheets-sheet 1 Dec. 15, 1936. J. J. KUNDIG 2,064,379

FLUID PRESSURE CONTROL SYSTEM l Original Filed Ja'n. l0, 1931 2` Shees-SheerI 2 I n tt v 105 67104' rLUrp PRESSURE coN'rRoL SYSTEM .Folin J. 'Kundig, New York, N. Y.

original application January io, 193i, serial No. 507,784. Divided and this application April 4, 1934, serial No. 718,951

My present invention relates to a fluid pressure control system in which a remote fluid motor may be automatically controlled by a manually operated iluid pressure control valve to operate in synchronism therewith and without having any mechanical interconnections for eecting the synchronized follow-up movement.

A further object of this invention is to provide a fluid pressure control valve having a primary and secondary control element and wherein the manual operationof the primary element acts through the intermediate of variating fluid pressures caused by said operation and acting upon to operate the secondary element intoopen orA fluid diverting position and to remain in such position as long as the primary` element is4 being manually operated, whereby the fluid motor is induced to operate in synchronism with the operation of the primary control element.

Another object is t`o provide means whereby the speed of operation of the fluid motor is maintained in constant synchronism with the speed of the manual operation of the primary elementl regardless oi' the load resistance to the fluid motor.

A further improvement consists of means for eiecting a retroactive inuence which is directly proportioned to the load resistance encountered.

by the motor and which is to be counteracted by the manual operation, whereby the operator has a cognizance or feel of the actual power4 generated'by the motor.

A further purpose of the invention is to pro- ,vide means, whereby the fluid motor is being 'f locked by enclosed pressure fluid tocheck reactions which may result from the motor driven mechanism and also to neutralize the retroactive influence upon the manual control means, when the latter are not being vactively operated.

In order that the operator may be able to operate the motor connected mechanism by manual power, in case of fluid pressure failure, I may l [provide an operative cponnection between the manual control means and the mechanism to be operated, on which, however, the operation of the control valve has no bearing whatsoever.

The invention as hereinafter morelfully Ydewould preferably use a hydraulic fluid as power' medium which is maintained in continuous circulation by a constantly operating pump and in a closed circuit under relatively low pressure. This pressure, however, will build up instantaneously when the fluid ow is being diverted from its normal circuitto actuate the iluid motor and in proportion to the resistance encountered by the latter -from the 4operated mechanism.

The invention, however, I do not consider as limited to the use voi a liquid power medium, inasmuch as it will be well understood vby those skilled in the art that similarresults can be obtained with the improvements as herein disclosed by using any other suitable fluid supply, such as air under pressure for' example.

While there is shown and described in detailv an embodiment of the invention, it is to be understood that variations in design of the fluid motor, the valve and its elements and the manual control means may be resorted to without departing from the spirit of the invention as expressed in the claims.

This application is a division of my co-pending application Serial No. (507,784, filed Jan. 10, 1931.

In the drawings, in which similar reference characters designate corresponding parts throughout the several views:-

Figure -1 illustrates a longitudinal sectional view of the-control valve in a. non-operating or neutral position;

Figure '2 illustrates a longitudinal section of the valve and showing the relationsbetwee'n the different elements vduring a manual operation to the right;

-Figure 3I isa longitudinal sectional View of the valve illustrating the different elements in their relations during a manual operation to the left;

Figures 4 and 5 are" diagrams showing the control valve in different practical applications in connection with fluid motors.

Fig. 6 shows a. portion of the valve as illustrated in Fig. 2, on an enlarged scale;

Fig. 7 is an enlarged view of the valve restoring means in a position as shown in Fig. 1;

Fig. 8 shows a spring washer; l

Fig. 9 illustrates a partial longitudinal section of the valve as shown in Fig. 3, with a slight alteration `of the port holes; and

Fig. 10 shows a washer plate.

In this construction of the control valve there is provided a .primary control element or valve sleeve which is slidingly fitted within a secondary valve sleeve 86, the latter in turn being -slidingly tted within the valve casing or housing 81. The outer valve sleeve 86 is internally counterbored `at one of its ends as at 88 while 85 is externally reduced in diameter as at 89. The shoulders |33 and |34 and the compression and expansion rings |35 and |36, respectively, located in grooves of the sleeves, serve as bearing for the spring washers |31. A compression spring 90, surrounding this end of the sleeve 85 and 1ocated between the spring washers |31, urges the sleeves in relatively opposite directions, and tends to yieldingly retain the latter in a normal neutral position. A relative sliding movement of the sleeves in either direction away from said neutral position will therefore compress said spring 90.

`The other end of the inner valve sleeve 85 is closed, and a hollow operating rod or stem 9| connected with the manually operable member, such as the lever 92, is movable therethrough, the end of said rod Within the valve sleeve 85 carrying a hollow head 93 slidably fitted within the valve sleeve. In spaced relation to this closed end of the valve sleeve, a collar 94 is threaded therein, a second collar 95 being also threaded in said valve sleeve and spaced from the'collar 94. The latter collar has a central orifice 96 which is normally closed by a valve ball 91 movable through said orifice to either side thereof. Washer plates 98 positioned in the recessed side faces of the collar 94 have parts engaging the valve. ball 91 and are respectivelyl held yieldingly' by springs 99 and' |00 against relative movement to retain the valve ball 91 in its normal position closing the orifice 96 and thereby forming the opposite relative and -independent fluid pressure chambers |01 and |21. 'I'he other end of the spring 99 is seated against a collar or washer plate |0| fixed to the rod |28 projecting from-the inner side of the head 93, While the other spring |00 is seated at its other end against the collar 95. This collar is'provided with a central opening |02 therethrough. 'Ihe compression of the spring 99 may be regulatedby the threaded portion of the rod |28 and the compression of the spring |00 is adjustable by the threadedollar 95.

The ball valve 91 presents a double acting check valve to regulate the fluid pressure differential between the chambers |01 and |21, such differential being directly proportioned to the tensions of the springs 99 'and |00. 'I'he spring 99, thereby, acts to check the fluid pressure from the chamber |01, which results in a similar effect as that obtained if two independent single and were employed. Presuming that the tensions of the respective springs 99 and |00 are properly` preadjusted to thereby effect a proportion of fluid pressure differential, between the two cham-A bers which is of the properratio to the thereto exposed opposite face areas of thev secondary sleeve 86, such fluid pressures will have a balancing .effect to hold the sleeve 86 in cooperation with ighe spring 90 in a neutral or non-'diverting posiion than the length of the'head 93, and a relatively strong coil spring |03 surrounds the spring 99 and yieldingly resists the initial movement of the head 93 relative to the valve sleeve. The wall of this head is provided 'with openings |04 therethrough in constant communication with the ports |05 in the wall of the valve sleeve 85. VThis end o f the valve sleeve is externally reduced in diameter'so as to provide the passage |06 affording communication between the interior of the -head 93 through openings |04 and ports |05 and the chamber |81l between the end of the outer The distance between the collar 94 and the` l closed end of the valve sleeve 85 is slightly greater valve sleeve and the closed end of the valve casing 81.

At the inner side of the collar 95, the wall of the valve sleeve 85 is provided at diametrically opposite sides of said valve with the port holes |08 and`|09 respectively, which are out of alignment with each other, said port holes in the normal position of the valve sleeves respectively registering with the relatively large port holes IIO in opposite sides of the secondary valve sleeve 86. Thus from reference to Fig. l, it will be understood that in this normal position of the valve sleeves, the pressure fluid has an unobstructed passage from the supply inlet through the primary and secondary valve sleeves to the return connection ||2. The supply connection is in communication with the internal longitudinally extending slot or chamber I3 formed in the valve casing, while the return connection ||2 'communicates with thev longitudinal extending slot |32. At one side of said valve casing in spaced relation from the chamber I3, the internal passage |4 is provided in the wall thereof in communication with the outlet connection II5, and with said passage the port I I6 in the wall of the sleeve 86 is in constant communication. The outlet II5 is also connected by the by-pass ||1 with the interior of the valve casing beyond the end 88 of the valve sleeve 86 and which is part of the chamber |21, such communication being normally closed by a spring seated valve I I8. The spring which presses upon the ball valve I |8 has for its sole purpose to insure proper seating of the latter and to prevent its rolling off when the control/ valve is in another position than horizontal, for example, such as that shown in Fig.

5. Other means, such as a guide for the ball may serve lthe same purpose. The outlet II5 is connected with one end of the piston cylinder I9.

The valve sleeve 85 is held against rotation relative to the sleeve 86 by the screw |20 threaded in the wall of the latter sleeve and having its inner end engaged in a slot or groove |2| formed in the outer surface of the valve sleeve 85. Similarly, a screw |22 threaded in the wall of the valve casing has its inner edge engaged in the slot o r groove |23 in the valve sleeve 86 to prevent rotative movement of the latter sleeve relative to the wall of the casing. In the manual operation of the control valve, as illustrated in Fig. 2, the primary control element or valve sleeve 85 is being shifted toward y the right within the secondary sleeve 86, and thereby acts as a plunger or piston between the .chambers |01 and |21 and will cause a variation `restriction of the orifice |09, whereby offering a resistance to the continuous flow of the fluid from the supply line to the return line ||2 which results in an instantaneous increase of fluid pressure in the chamber I 21. The check valve I I8 will thereby be opened to admit the pressure fluid to the cylinder H9.

Such increased fluid pressure will also act upon the righthand face areas of the sleeve 86, tending to further shift the latter towards the left relative to the, sleeve 85 and against the tension of spring 90.

Upon continuation of the initial operating speed of the sleeve 85, the increase of volume of the chamber |01 will be compensated by the inflowing fluid from the chamber |21 to thereby maintain the established fluid pressure differential between the chambers |01 and |21, presuming that the capacities of the springs 99 and |03 are in correct 'proportion to thereby properly meter said inflowing fluid.

If the manual operating speed of the rod 9| is maintained constant and the load resistance upon the piston |29 remains constant, the fluid pressure in chamber |21 willalso remain constant. The sleeve 86 will then follow the movement of sleeve 85 towards the right by the fluid pressure influence upon its relatively bigger lefthand area. Obviously the areaof the restricted port |09 will remain constant during the unitary movement of the sleeves 85 and 86 with the result that aA constant amount of pressure fluid will be diverted upon the piston |29 and effecting the latter to operate at a constant speed in proportion to the manual operating speed of the rod 9|.

Assuming that the uniform operation of the rod 9| is continued and the sleeves 85 and 86- shift in unison therewith towards the right and the load resistance upon the piston |29 should, for example, increase, then the fluid pressure in the chamber |21 will obviously increase also. Such increase of fluid pressure acting against vthe right end face area of the sleeves 86 and 85 willtend to lshift the latter to theleft relatively to the head 93 vand compress the spring |03'. The movement `of sleeve 86 will be retarded and further shifted towards the left upon the sleeve 85, thereby further compressing the spring 90. The port |09 will be further restricted to thereby automatically regulate the passage areal for the fluid under increased pressure and whereby the amount of diverted fluid, upon the cylinder |I9 is maintained constant, resulting in constant operating speed of the piston |29.

In the movement of sleeve 85 relatively to the head 93,' the spring 99 will also be further compressed, resulting in a bigger opposition of ball valve 91 to the increased fluid pressure inchamber |21 and thereby regulate the effective passage I area of orifice 96 for the compensating fluid entering the chamber |01, thereby automatically' although never reaching the potentiality of the fluid pressure in chamber |21. A difference of fluid pressures between the two chambers, during the operation of the valve, will always exist in proportion to the tension of spring 99. Since said variation of the fluid pressure differential is caused by the volumetric changes of vthe capacity of chamber |01, I may obtain anydesired sensitiveness of the secondary sleeve 86 responding tol the manual operation of the sl-eeve 85 by enlarging the outside 'diameter of the ysleeve 85 to thereby increase its volume, or by reducing the outside diameter of the sleeve 86 to thereby reduce its face area which is exposed to the chamber. A small shifting movement of the relatively big body of the sleeve 85 will therefore result in.

an instantaneous and big shifting movement of the secondary sleeve 86. This presents a highly desirable feature of the control valve, as practically no lost motion for overlapping the port holes will be perceived. Thereby the resulting rapid restriction of the port |09 of the inner valve sleeve wall will tend to cut oi the ilow of the pressure fluid to the return connection I|2. Thus pressure builds up instantly Within the chamber |21 and overcomes the slight resistance of the ball valve ||8 to act through the intermediate of conduit upon the piston within the cylinder ||9.

Obviously the pressure of the continuously inowing hydraulic fluid will automatically adjust itself to the load resistance encountered by the piston |29 and therefore be directly proportional to the power output of the latter. Since the right end face of the sleeve 85 together with the right end surface of the collar 95 and the collar 94, are exposed to the actuating fluid pressure, such fluid pressure will counteract the manual shifting movement of the sleeve 85 and thereby impress thedesired proportional feel of the fluid pressure variations within the-motor ||9 upon the lever or other manually operable part 92.

As shown in Fig. 2 of the drawings, the pressure fluid within the chamber |21 also has free passage through the opening |02 and acts against the valve ball 91 to move the samein one direction against the action of the spring 99 so that .the pressure fluid may pass thro-ugh the orice 96, openings |04 and ports |05 and thus enter chamber |01.

If the primary sleeve 85, by an initial manual operation of the control rod 9|, is moved to the right at a slow rate of speed, the pressure variation between the two chambers will be little, since the vacuum created by augmenting the volume of chamber |01 will be low and in proportion to the tension of the relatively weak spring 99, as the pressure exerted from the manual control rod 9| upon the spring 99 will obviously be low at slow operating speed. The ball valve 91, in its throttling effect upon the fluid passing through orifice 96 will thereby regulate the amount of compensating fluid flowing into chamber |01-in a given time period to thereby maintain said vacuum .in proportion to the speed of manual operation. The secondary sleeve 86 will thereby be shifted only ay short distance against the resistance of the spring 90 and oppositely relative to the initial movement of the sleeve 85 and thereby only partly obstructing the orice |09. Part of the pressure fluid from the continuous supply entering through conduit will then pass through orifice |09 and to the discharge I2, while the other part will be forced through conduit ||5 to actuate the piston |29 at a relatively slow rate of speed. Upon continued slow operation of the sleeve 85, the sleeve 86 will remain in its assumed and relative position thereto and move in unison therewith under the influence of the pressure, uid entering from the opposite' 'chamber |21 and thereby maintain saidI partial obstruction .of the orifice |09 with the result that the piston |29 will maintain its slow actuating speed in synchronism with the slow manual operation of the control rod 9|. f

' If the primary sleeve 85 is being operated towards the right at a higher rate of speed, there will then be a bigger variation of the fluid pressures. between thechambers A|01 and` |21. VThe compensation of the more rapid initial increase of volume in chamber |01, by the fluid entering through orifice 96, will be more delayed in a given time period due to the inertia of the inflowing fluid which results in aA bigger shifting movement of sleeve 86 towards the left and a bigger restriction of the port |09.

The resulting higher fluid pressure in chamber |21 will also shift the primary sleeve 85 towards the left relatively to the head 93 and compress the spring |03 together with the spring 99 whereby to increase the throttling effect of the valve 91 upon the inflowing compensating fluid to adjust the vacuum in proportion-to the higher speed of manual operation. Thereby the resulting bigger or full obstruction of the port |09 will effect the diversion of a bigger or of the whole amount of pressure fluid supply upon the piston |29 and cause the latter to move ata higher rate of speed and in synchronism with the speed of the manually operated rod 9|.

The retroactive eifect upon the sleeve 85 from the increasing fluid pressure within the chamber |21 resulting from the restriction or obstruction of the port |09 and caused by the above described operations will tend to retard the movements of the sleeve 85 relatively to the movements of the operating rod 9|, and respectively of the head |06, due to the movable relation therebetween and the sleeve 85 which results in a compression of the spring |03 carried by the head |06. The pressure of the spring |03 is preadjusted by the threaded collar 94 to allow maximum sliding movement of the head |06 relative The relative positions which the different elements have assumed during the above described operation are more clearly shown in Fig. 6, which is an enlarged illustrated view of a part of Fig. 2.

The effective area of the orifice 96 through which the pressure fluid may pass is therefore automatically metered or adjusted bythe influence of spring 99 upon valve 91 that the quantity of fluid entering chamber |01 during a given time period and a given speed of operation re mains constant regardless of the magnitude of fluid pressure in chamber |21, thus maintaining a constant relative proportion of fluid pressures v in the chambers |01 and |21 to keep the secondary valve sleeve 86 in its assumed operating position during a continued shifting movement of the primary control element 85.

In the operation of the control valve the maximum sliding movement of the secondary sleeve 96 relative to the primary sleeve 85 is limited by the stop ||2 engaging one end of the channel or groove |2| and only sufficient to cut off communication between the chamber |21 and the return connection ||2. During such movement of the inner valve member and the further follow-upV movement of the outer valve member, communication between the passage ||4 and the interior of the valve member 85 is closed by the wall of the valve member 85 closing the port` ||6.

Due to the effect of the check valve 91 caused by the proportionate compression of its spring |03, the uid pressure in the chamberl |01 during the operation of the valve to the right, will always be proportionately lower than the uid pressure in the chamber |21. The retroactive influence v upon the manually operated primary element 85 will therefore always be towards .the left or against the latters movement, such effect being markedly increased by the substantially bigger face area of the combined elements 85, 94-and 91 which are exposed to the fluid pressure in chamber |21 as against the opposite face area of the sleeve 85 which has a smaller outside diameter and is further reduced by the cross area of the operating rod 9|.

The substantially bigger face area of the secondary sleeve 86 which is exposed to the chamber |01 insures an effective operation towards the right an'd against the fluid pressure influence in chamber |21 upon its right end face area which is markedly smaller due to the enlarged inside diameter of the pressure exposed sleeve.

Concurrently with the stopping of the manual shifting of the sleeve 85 to the right, .the fluid pressure flowing from chamber |21 through the orifice 96 and into chamber |01 will act upon 'the left side face of the secondary valve sleeve 86 to further shift the latter in cooperation with the spring 90 towards a neutral position. Due to the checking effect of the valve 91 caused by the spring 99 against the flow of the pressure fluid from chamber |21 to chamber |01, the fluid pressure in chamber |21 will drop slightly below the fluid pressure in chamber |01 during a further opening of the passageway through ports |09 and Thus the resulting slight pressure differential between the two chambers in cooperation withv the pressure effect of the valve centering spring 90 will finally shift the sleeve 86 to a position relative to sleeve 85 as indicated in Fig. 1, and reestablisha neutral or non-diverting position.

When the manually operable primary control element 85 vis moved in the opposite direction additional pressure is produced in chamber |01,

by the reduction of the latters volume, thus' destroying the balance of the fluid pressure 'upon and forcing the outer valve sleeve 86 in the reverse direction and until port I6 is uncovered by the inner valve sleeve and port |09 of said valve sleeve isin registering relation with the lower port in the outer sleeve and in communication through chamber |32 with the return connection I2. ,'I'hus, as seen in Fig. 3 of the drawings, the pressure fluid may now freely pass from ".the cylinderA ||9 through the connection ||5,

passage ||4 and around the-reduced end 8 9 of the 'a inner valve sleeve into chamber` |21 and hence through port |09 to the return connection ||2. The amount of travel of the sleeve 86 relative to sleeve 85 which determines the quantity of Apressure fluid admitted to chamber |21`from the line through port ||6, is again directly proportional to the speed at which the primary valve is being operated. A slow initial move-. ment of the sleeve 485 towards the left will obviously elect a slow volumetric decrease of the chamber |01 and a. relatively slight increasel of fluid pressure therein since the pressure fluid may escape through the orifice 96 by pressing the ball valve 91 towards the right against the small resistance of spring |00. Thereby the effected variation of fluid pressure influence upon the sleeve 86 in the chamber |01, will therefore no more be counterbalanced by the relatively lower relative to and in unison with the sleeve 85 by thev pressure influence of spring 90.,` The effective area of passage which is thereby uncovered of the port ||6 will also remain constant which results in a constant flow of pressure fluid from the conduit |I5 to the discharge ||2 and of a relatively low capacity. vThe piston |29 will therefore be moved in an opposite direction by the load resistance and at proportionate speed or in synchronism with the speed of the manually operated sleeve 85. i

It will be understood that a more rapid operation of the sleeve towards the left will produce a relatively higher fluid pressure in the chamber |01 due to the greater volume of pressure fluid to be thus forced through the orifice 96. 'I'he thereby assumed position of sleeve 86 relative to sleeve 85 will cause a bigger opening of port H6, permitting the piston |29 to force a bigger amount of pressure fluid to the discharge conduit ||2 in the same time period and, therefore, again operate in synchronism with the more rapidly moving primary control element 85. The communication between the ports |08 and ||0 is shut off during the operating position. Should the control valve be used in conjunction with a single acting actuator such as illustrated in Fig. 4, the port |08 would then be sufficiently enlarged to maintain free passage of the pressure fluid from the supply I I to the return l |2 during the discharge period, as illustrated in Fig. 8. In such relative movement of the valve sleeves as last explained, the spring is of course placed under compression.

Upon an arresting of the manual shifting operation of sleeve 85 in the reversed direction, the secondary valve sleeve 86 will be quickly shifted to the left and towards neutral position by the influence of the spring 90 which also forces by its action some of the fluid pressure in chamber |01 against the relatively small resistance of ball valve 91 and through the orice 96 into chamber |21, thereby re-establishing the balancing effect of the fluid pressures in the chambers |01 and |21 upon vthe secondary valve sleeve 86 which again resumes a neutralposition relative to sleeve 85 as shown in Fig. 1 of the drawings.

From the foregoing it will be understood that if the capacities of the divers springs are properly effectively checked by the enclosed fluid pressure in said cylinder. A retroactive influence from the pressure condition in the power cylinder andupon the manually controllable valve sleeve 85 is, therefore, possible only during an active manual operation of said sleeve 85.

The valve as described may be used for controlling the fluid pressure effect upon a single or one-way acting fluid motor or piston cylinder such as indicated in Fig. 4 'of the drawings. Such a device may, for example, be applied to automotive vehicles for the operation of the brakes, the .piston in the singleacting cylinder 9 being operatively connected with the load shaft |24 of the brake mechanism. Of course, it will be understood that a foot-actuated pedal may be substituted for the hand lever 92 shown in the figure. Normally when the brakes are not applied or when maintained stationary in an applied position and the valve mechanism is in .neutral position, there is a free and unobstructed continuous circulation of the hydraulic fluid medium between the continuously operating pump |30 and the supply tank |3|, the pump being driven through a suitable connection by the vehicle engine.

By altering the construction and without departing from the Spirit of the present invention, the valve may be variously modified to have a double acting effect upon the fluid pressure diversion or I may apply two valves of the illustrated type for'controlling the fluid pressure effeet upon two single and oppositely'acting or a double acting actuator. In Fig. 5, I have illustrated an exemplary arrangement, wherein two of the control valves are emplo'yed in conjunction with a steering mechanism of an automotive vehicle, the primary control elements of the valves being actuated by the manually operated steering post. In this case, a double-acting power cylinder may be employed as shown in Fig. 5,

vof which the opposite ends` are connected with the outlets ||5 of the respective valves. The steering lever 22 in this case has a lost-motion connection such as that indicated at |25 with the operating connections or drag link |26 between the actuator and the steering linkage or other part to ybe actuated. The lost-motion may be cushioned by suitable oppositely acting springs located in the enlarged portion of the part |26.

The sole purpose of the steering lever 22 is to transmit manual power which can be added to the power of cylinder ||9 or to operate the steeringmechanism by sole manual power in case of fluid pressure supply failure.

Due to the fact that the control valve as described herein, operates to open or fluid diverting position upon an initial movement of the manually operable control member and remains in such open position during a continued mobile manual operation, and to close automatically and simultaneously with the stopping of the manual control, the mechanism or actuator to be actuated by the divertediiuid pressure will be caused to operate in perfect synchronism with the movements of the manual operating means. In other words, a predetermined linear motion in one direction of the control rod 9| will automatically cause a predetermined and relative movement of the piston |29 in the power cylinder |19, which represents a remote control system for synchronous fluid pressure actuation without mechanical interconnections for follow-up movement.

While I have thus disclosed two different applications of the described embodiment of the control valve, it will be apparent that the device might also be incorporated in various other arrangements and applied to numerous different l uses.

I claim:

l1. In a fluid pressure control valve having a normally closed communication with a fluid mo'- tor, supply and exhaust ports, a supply of pressure fluid, a housing, a movable element in said I housing forming a pair of independent and relatively opposite fluid pressure chambers, a movable valve element for controlling the flow ofv said pressure fluid and having relatively opposite portions exposed to the fluid pressures in said opposite chambers, and manual control means for moving said movable element to vary the volume of and thereby lthe fluid pressure differential in said chambers whereby to operate said valve element to divert said pressure fluid to said motor. l

2. In a fluid pressure control valve, a valve casing having a. supply port, a discharge port and a normally closed feed port communicating with a fluid motor, a supply of pressure fluid, an oppositely closed cylinder in said casing and having a movable element to form a pair `of independent and relatively opposite fluid pressure chambers, a normally neutral positioned valve element for controlling said port and having relatively opposite portions exposed to the fluid pressures in said opposite chambers, manual control means for moving said movable element to effect a differential of fluid pressures between said chambers whereby to operate said valve element into an operating position to divert pressure fluid to said motor, means whereby to subject one of said chambers to the pressure influenee of the motor actuating fluid pressure to thereby effect a retroactive influence against the movement of said movable element in direct proportion to the motor power, a fluid passage between said two chambers and a spring pressed valve for controlling the flow of pressure fluid through said passage and means whereby also to subject the spring of said valve to said retroactive influence to control the area of said passage in proportion to said actuating fluid pressure and thereby control said fluid pressure differential in proportion to the power required to operate said manual control means, said spring pressed valve acting to admit pressure fluid from the actuating fluid pressure subjected chamber to the opposite chamber for balancing the pres- `sures therebetween to thereby cause said valve element to move to neutral position concurrently with the stopping of said manual operation.

3. In a fluid pressure control valve having an oppositely closed housing, a movable valve element normally held in a non-operating position by resilient means, a plunger in said housing forming a pair of independent and relatively opposite fluid pressure chambers therein, said valve element having relatively opposite portions exposed to said opposite chambers, a supply of pressure fluid, normally open supply and exhaust ports, a normally closed communication between the control valve and a fluid motor, manual control means for moving said plunger whereby to change the volume of and thereby to effect a g fluid pressure differential between said chambers to thereby move said valve element into operating position whereby to restrict the effective passage area of said exhaust port in proportion to said differential and to divert an amount of pressure fluid to actuate said motor, a uid passage connecting said chambers, a spring pressed valve for controlling the flow of compensating p1 essure fluid through said passage to maintain said differential constant and to thereby maintain said valve element in said operating position during a continued operation of said manualy control means at constant speed whereby also maintaining said exhaust port area restriction and the amount of diverted motor actuating fluid constant to cause said motor to operate at a speed proportional to the operating speed of said manual control means, means whereby to subject one of said chambers to the pressure influence of the motor actuating fluid pressure to thereby control the operating position of said valve element, and means whereby to subject the spring of said passage controlling valve to the pressure influence of the motor actuating fluid pressure for restricting said passage in proportion to said actuatlng fluid pressure to thereby also control said differential and the obstruction of said exhaust port in proportion to the resistance encountered by said motor.

4. In a fluid pressure control valve having an oppositely closed housing, a movable valve element normally held ina non-operating position by resilient means, a plunger in said housing forming a pair of independent and relatively opposite fluid pressure chambers therein, said valve element having relatively opposite portions exposed to said opposite chambers, a supply of pressure fluid, normally open supply and exhaust ports, a normally closed communication between the control valve and a fluid motor, manual control means for moving said plunger whereby to change the volume and thereby effect a fluid pressure differential between said chambers to thereby move said Valve element into operating position whereby to restrict the effective passage area of said exhaust port in proportion to said differential and to divert an amount of pressure fluid to actuate said motor, a fluid passage connecting said chambers, a spring pressed valve for controlling the flow of compensating fluid through said passage to maintain said differential constant and to thereby maintain said valve element in said operating position during a continued operation of said manual control means at constant speed whereby maintaining said exhaust port restriction and the amount of diverted motor actuating fluid constant to cause said motor to operate at a speed proportional to the operating speed of said manual control means, means whereby to subject one of said chambers to the pressure influence ofv the motor actuating fluid pressure to thereby effect a retroactive iniiuence against the manual operation of said plunger which is proportional to the motor power and to control the operating position of said valve element and means whereby to subject the spring of said passage controlling valve to said retroactive influence for restricting said passage and thereby control said differential and the restriction of said exhaust port in proportion to said motor actuating fluid pressure.

5. In combination, a. fluid motor connected with a part to be actuated, a supply of pressure fluid and a control valve for said supply having a valve casing, a supply port, an exhaust port and acnormally closed motor feed port, a movable plunger in said casing forming a pair of inclependent and relatively opposite fluid pressure' chambers, a valve element movable under the influence of the fluid pressure differential between said two chambers, manual control means to move said plunger whereby to vary the volumes of said chambers and thereby also vary the fluid pressure differential to operate said valve element into an operating position whereby tending to close said exhaust port and to divert an amount of pressure fluid for actuating said motor, a fluid passage between said chambers having a spring pressed valve for controlling the flow of compensating fluid through said passage to maintain said differential constant during a constant manual operating speed of said plunger vto thereby divert a constant amount of pressure fluid causing said' motor to operate at -constant speed in proportion to the manual operating speed, means for `subjecting one of said chambers and thereby one side of said valve element to the motor actuating fluid pressure influence for also controlling the operating position of said valve element in proportion to said actuatingfluid pressure, means for subjecting the spring of said passage controlling valve to the motor actuating fluid pressure said motor connected part for manually operating the latter in c ase of fluid pressure supply failure.

6. In a fluid pressure control valve having a movable valve element, an oppositely closed cylinder and a primary control element slidingly fitting therein and forming a pair of independent and opposite relative fluid pressure chambers, said valve element having opposite relative face areas directly subjected to the influence of the fluid pressure in the correspondingly opposite chamber, said valve element having normally a neutral or non-fluid diverting position under the balanced influence of the fluid pressures in said chambers, manual operating means for shifting said primary control element to cause variations of fluid pressure in said chambers and thereby effecting a movement of said `valve element to operating position, and Valve means responsive to the fluid pressures in said chambers and incorporated with said primary control element for automatically effecting a return movement of said valve element to neutral position and under the influence of the supply fluid pressure and to re-establish said balanced influence simultane- ,ously with the stopping of the manual shifting operation.

'7. A fluid pressure control valve, a valve casing having supply, discharge and feed ports, said feed port communicating with a part to be actuated, asupply of fluid pressure, a movable valve ele-4 operating means for shifting said primary control element in one direction to cause variations of fluid pressure in said independent chambers and thereby effecting a movement of said valve element into a position to direct the pressure fluid from said supply port to said feed port and to power required for actuating said part, and means responsive to the fluid pressures in said chambers and incorporated with said primary control element for automatically effecting a return movement of said valve element to neutral position and under the influence of said supply fluid pressure and said resilient means to re-establish said balanced influence simultaneously with the stopping of the manual shifting operation, said valve element being operated in an opposite direction from said neutral position by the reversely unbalanced fluid pressure influence to thereby open communication between said feed port and said discharge port upon a reversed manual operation of said control member.

8. A fluid pressure control valve, a valve casing having a supply, discharge and feed port, said feed port communicating with a part to be actuated, a supply of fluid pressure, a movable valve element in said casing, an oppositely closed cylinder having, a primary control element slidingly fitting therein and forming a pair of independent and relative opposite fluid pressure chambers, said movabler valve element having relative opposite face areas exposed to the influence of the fluid pressures of the corresponding chambers, said faceareas and the fluid pressures in said chambers having such correlation to effect a balancing influence upon said valve element and to thereby hold the latter in cooperation with resilient means normally in a neutral or non-fluid diverting position, manual operating means operatively connected to shift said control element and to thereby produce a variation of fluid pressures in said chambers acting to move said valve element into a position to direct the pressure fluid from said supply port to said feed port for actuation of said part, means directly influenced by said actuating fluid pressure to impress a retroactive influence against the manual shifting of said control element by varying the fluid'pressure in the chamber located oppositely to the shifting movement in said direction and in direct proportion to the power required for said part actuation, and a passageway in said control element connecting said opposite chambers, a valve movable in two directions and carried by said control element and having oppositefaces exposed to the fluid pressures in the corresponding opposite chambers, springs acting oppositely upon and tending to hold said valve in a position to close said passageway, means for directly subjecting one of 'said springs to said retroactive impression which is applied upon the manual operating means, whereby the flow of pressure fluid between said chambers is automatically regulated to maintain the fluid pressures in said chambers constantly proportional to said rst produced variation of pressure during a continued manual operation of the control element in said direction at constant speed and under constant pressure resistance, and said valve acting to automatically vary the fluid pressures in said chambers to restore said balancing influence and tothereby effect an operation of said valve element in an opposite direction and to neutral position concurrently with the stopping of the manual operation, and said valve element being further operated beyond said neutral position by a reversed variation of fluid pressures in said cham, bers during a reversed manual operation of said control element to thereby open communication between said feed port and said discharge port. 9. In a uid pressure control valve having an 'oppositely closed housing, a movable valve ele-` ment normally held in a non-operating position by resilient means, a movable element forming a -pair of independent and relatively opposite fluid of and effect thereby a iluid pressure diierential l between said chambers to move said valve element into operating position whereby restricting .the eective passage area of said exhaust port in proportion to said differential and to divert an amount of pressure uid to said motor, a fluid passage connecting said chambers, a spring pressed valve for controlling the flow of compensating pressure uid through said passage to maintain said differential constant and to thereby maintain said valve element inv said operating position during a continued'operation of said manual control means at constant speed whereby maintaining said exhaust area restriction and the amount of diverted pressure uid upon said motor also constant to cause the latter to operate at a speed proportional to the operating speed of said manual control means.

JOHN J. KUNDIG. 

